Stirling heat pump systems and their control methods

Abstract

This application provides a Stirling heat pump system and its control method, including a Stirling compressor and a gas handling device. The Stirling compressor has a cold end and a hot end capable of heat exchange with a working fluid. The gas handling device is disposed on the outer wall of the Stirling compressor and includes a cold-end heat exchanger capable of heat exchange with the cold end and a hot-end heat exchanger capable of heat exchange with the hot end. The gas first flows through the cold-end heat exchanger for cooling and dehumidification, and then flows through the hot-end heat exchanger for heating. The Stirling compressor provided in this application, combined with the gas handling device disposed on the outer wall of the Stirling compressor, enables the working fluid to absorb heat from the gas through the cold-end heat exchanger, causing the moisture in the gas to liquefy and condense, thereby achieving cooling and dehumidification. Simultaneously, the working fluid also releases heat to the gas through the hot-end heat exchanger, causing the gas to heat up, achieving high-temperature heating. That is, the Stirling heat pump system can simultaneously achieve both low-temperature dehumidification and high-temperature heating.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat pump systems, in particular to a Stirling heat pump system and a control method thereof. BACKGROUND

[0002] A heat pump system is a high-efficiency energy utilization technology that can absorb heat from the natural environment and then transfer it to a space or medium that needs to be heated. The core principle of a heat pump system is to use a heat pump cycle to absorb heat from a low-temperature heat source in an evaporator through a refrigerant (also known as a refrigerant or working medium), and then release heat in a condenser, thereby achieving heat transfer.

[0003] In industrial or commercial applications, heat pump type drying equipment has a significant energy efficiency advantage compared to traditional electric heating drying equipment. Heat pump type drying equipment realizes low-temperature heat absorption and high-temperature heat release through the circulation of refrigerant. In the evaporator, the refrigerant absorbs heat from the surrounding air and evaporates, and then is compressed by the compressor to increase its temperature and pressure. However, the traditional refrigerant vapor compression cycle has certain limitations. When the refrigerant approaches its critical temperature, its compression efficiency will decrease, resulting in a decrease in the overall energy efficiency of the heat pump system. SUMMARY

[0004] The embodiments of the present application provide a Stirling heat pump system and a control method thereof, aiming to improve the problem of low energy efficiency of the heat pump system.

[0005] In a first aspect, the embodiments of the present application provide a Stirling heat pump system, comprising a Stirling compressor and a gas treatment device; the Stirling compressor has a cold end capable of heat exchange with a working medium and a hot end; the gas treatment device is arranged on the outer side wall of the Stirling compressor and comprises a cold end heat exchanger capable of heat exchange with the cold end and a hot end heat exchanger capable of heat exchange with the hot end; wherein the gas can first flow through the cold end heat exchanger for cooling and dehumidification, and then flow through the hot end heat exchanger for heating and temperature rise.

[0006] In some embodiments, the gas treatment device comprises a shell; the shell is arranged around the Stirling compressor, and the shell and the outer side wall of the Stirling compressor jointly form a dehumidification cavity and a heating cavity in communication; wherein the cold end heat exchanger is arranged in the dehumidification cavity and connected with the cold end, and the hot end heat exchanger is arranged in the heating cavity and connected with the hot end.

[0007] In some embodiments, the gas treatment device further comprises an air inlet pipeline and a fan; the air inlet pipeline is in communication with the dehumidification cavity; and the fan is arranged on the air inlet pipeline and used to blow the gas into the dehumidification cavity.

[0008] In some embodiments, the gas treatment device further comprises:

[0009] a filter disposed on the air inlet pipeline and located upstream of the fan along the air flow direction of the air inlet pipeline; and / or

[0010] a buffer disposed on the air inlet pipeline and located between the fan and the dehumidification chamber.

[0011] In some embodiments, the gas treatment device further comprises an air outlet pipeline and a regulating valve, one end of the air outlet pipeline is in communication with the heating chamber, and the other end is configured to be in communication with the production process line; the regulating valve is disposed on the air outlet pipeline.

[0012] In some embodiments, the gas treatment device further comprises a waste heat recovery device, the waste heat recovery device has a first air inlet end, a first air outlet end, a second air inlet end, and a second air outlet end, the first air inlet end is in communication with the dehumidification chamber, the first air outlet end is in communication with the heating chamber, the second air inlet end is configured to be in communication with the production process line, and the second air outlet end is in communication with external air or the air inlet pipeline.

[0013] In some embodiments, the gas treatment device further comprises a liquid collecting tank, a drain pipeline, and a drain valve; one end of the drain pipeline is in communication with the dehumidification chamber, and the other end is in communication with the liquid collecting tank; the drain valve is disposed on the drain pipeline and located between the dehumidification chamber and the liquid collecting tank.

[0014] In some embodiments, the Stirling compressor is at least one of an α-type Stirling compressor, a β-type Stirling compressor, and a γ-type Stirling compressor.

[0015] In some embodiments, the Stirling compressor is a β-type Stirling compressor, the β-type Stirling compressor comprises a cylinder, a sliding element, a piston, and a driving mechanism; the cylinder is filled with a working medium; the sliding element is slidably disposed in the cylinder, a compression chamber is formed between the sliding element and the inner wall of the cylinder, and the working medium in the compression chamber is used for heat exchange with the hot end; the piston is slidably disposed in the cylinder, an expansion chamber is formed between the piston, the sliding element, and the inner wall of the cylinder, and the working medium in the compression chamber is used for heat exchange with the cold end; and the driving mechanism is connected with the sliding element and the piston, and the driving mechanism is used to drive the piston and the sliding element to make reciprocating linear motion in the cylinder, so as to drive the working medium to flow reciprocatingly between the compression chamber and the expansion chamber.

[0016] In some embodiments, the cylinder includes a cylinder body and a cylinder shell, the sliding member and the piston are arranged in the cylinder body, the cylinder body is formed with the expansion chamber and the compression chamber, and the cylinder shell is formed with a working medium flow path, one end of the working medium flow path is communicated with the compression chamber, the other end of the working medium flow path is communicated with the expansion chamber, and the regenerator is arranged on the cylinder shell and can exchange heat with the working medium.

[0017] In some embodiments, the beta-type Stirling compressor further includes a first telescopic member and a second telescopic member, the first telescopic member is telescopically arranged on the piston to change the volume of the expansion chamber, and the second telescopic member is telescopically arranged on the sliding member to change the volume of the compression chamber.

[0018] In some embodiments, the first telescopic member is telescopically arranged along the driving direction of the driving mechanism relative to the piston, and / or the second telescopic member is telescopically arranged along the driving direction of the driving mechanism relative to the sliding member.

[0019] In some embodiments, the phase angle between the piston and the sliding member is α, and the α satisfies 60°≤α≤90°, and / or,

[0020] The driving mechanism includes a rhombus driving mechanism.

[0021] In a second aspect, the embodiments of the present application provide a control method of a Stirling heat pump system, applied to the Stirling heat pump system as described above, and the control method includes:

[0022] Obtaining a target output parameter of the Stirling heat pump system;

[0023] Adjusting the volume of the compression chamber and / or the expansion chamber of the Stirling compressor according to the target output parameter.

[0024] In some embodiments, the target output parameter includes a target output gear, and the step of adjusting the volume of the compression chamber and / or the expansion chamber of the Stirling compressor according to the target output parameter includes:

[0025] Obtaining a current gear of the Stirling heat pump system;

[0026] When the current gear is lower than the target output gear, reducing the volume of the compression chamber and / or increasing the volume of the expansion chamber;

[0027] When the current gear is higher than the target output gear, increasing the volume of the compression chamber and / or reducing the volume of the expansion chamber.

[0028] In some embodiments, the target output parameter comprises a target output temperature, and the step of adjusting the volume of the compression chamber and / or the expansion chamber of the Stirling compressor according to the target output temperature comprises:

[0029] obtaining a current temperature of the gas output by the Stirling heat pump system;

[0030] when the current temperature is less than the target output temperature, reducing the volume of the compression chamber and / or increasing the volume of the expansion chamber;

[0031] when the current temperature is greater than the target output temperature, increasing the volume of the compression chamber and / or reducing the volume of the expansion chamber.

[0032] The Stirling heat pump system and the control method thereof in the embodiments of the present application, the Stirling heat pump system comprises a Stirling compressor, the Stirling compressor is a circulating compressor, which works based on the Stirling cycle principle, can realize heat transfer under a larger temperature difference, so that the Stirling heat pump system can work at a lower input temperature and provide a higher output temperature, which helps to improve the heat exchange efficiency and reduce energy consumption. The working medium flows in the Stirling compressor, and the Stirling compressor is combined with a gas treatment device arranged on the outer wall of the Stirling compressor, which can realize heat absorption of the working medium in the cold end heat exchanger to the gas, so that the water in the gas is liquefied and condensed, thereby realizing cooling and dehumidification; the working medium also releases heat to the gas in the hot end heat exchanger, so that the gas is heated to realize high-temperature heating. That is, the Stirling heat pump system can realize both low-temperature dehumidification and high-temperature heating.

[0033] The application of the control method of the above Stirling heat pump system in the embodiments of the present application can finally realize accurate adjustment of the temperature of the gas output by the heat pump system by obtaining the target output parameter to change the volume of the compression chamber and / or the expansion chamber, and the heat pump system can provide gas at different temperatures according to different application requirements. In industrial production, the temperature of the gas can be adjusted according to the needs of different process flows, for example, high-temperature gas can be used for disinfection and sterilization, which meets the diversified industrial application requirements. BRIEF DESCRIPTION OF DRAWINGS

[0034] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed in the embodiments or the prior art description will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor.

[0035] Figure 1 a structural schematic diagram of a Stirling heat pump system provided by an embodiment of the present application;

[0036] Figure 2 Part structure schematic diagram of a Stirling heat pump system provided by an embodiment of the present application;

[0037] Figure 3 Part structure schematic diagram of a Stirling heat pump system provided by an embodiment of the present application from another direction;

[0038] Figure 4 Control method schematic diagram of a Stirling heat pump system provided by an embodiment of the present application.

[0039] Legend of reference signs:

[0040] 100, Stirling heat pump system; 10, Stirling compressor; 10a, cold end; 10b, hot end; 11, cylinder body; 111, cylinder main body; 111a, expansion cavity; 111b, compression cavity; 112, cylinder shell; 113, regenerator; 12, sliding member; 13, piston; 14, driving mechanism; 15, first telescopic member; 16, second telescopic member; 20, gas processing device; 21, cold end heat exchanger; 211, air inlet pipeline; 212, water outlet pipeline; 22, hot end heat exchanger; 221, air outlet pipeline; 23, shell; 23a, dehumidification cavity; 23b, heating cavity; 24, fan; 25, filter member; 26, buffer member; 27, regulating valve; 28, waste heat recovery device; 281, first air inlet end; 282, first air outlet end; 283, second air inlet end; 284, second air outlet end; 29, liquid collecting tank; 291, water outlet valve;

[0041] 200, Production process line body. DETAILED DESCRIPTION

[0042] In order to make the objects, technical solutions and advantages of the present application clearer, the present application will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and should not be used to limit the present application.

[0043] Please refer to Figures 1 to 3The embodiment of the present application provides a Stirling heat pump system 100, which comprises a Stirling compressor 10 and a gas treatment device 20. The Stirling compressor 10 is a kind of cycle compressor, which works based on the principle of Stirling cycle, and comprises four main steps: isothermal expansion, isochoric cooling, isothermal compression and isochoric heating. The heating and cooling processes of the Stirling compressor 10 are carried out outside the Stirling compressor 10, which means that the working medium is not combusted inside the Stirling compressor 10. Due to the configuration of external heating and cooling, the Stirling compressor 10 can achieve higher thermal efficiency, because it can more effectively control the heat source and the cooling process. The Stirling compressor 10 can achieve higher output power under lower energy consumption. And because there is no internal combustion process, the noise and vibration of the Stirling compressor 10 are lower during operation.

[0044] The Stirling compressor 10 circulates the working medium, which undergoes compression and expansion processes inside the Stirling compressor 10. In the compression process, the working medium is heated and the pressure is increased; in the expansion process, the working medium is cooled and the pressure is reduced, that is, the Stirling compressor 10 has a cold end 10a and a hot end 10b which can exchange heat with the working medium. The Stirling compressor 10 can use a variety of different working media, which can be helium, argon, air, nitrogen or their mixed gas.

[0045] The gas treatment device 20 is arranged on the outer side wall of the Stirling compressor 10, which helps to optimize the overall space layout of the Stirling heat pump system 100, so that the system is more compact and convenient for integration and installation. The gas treatment device 20 comprises a cold end heat exchanger 21 which can exchange heat with the cold end 10a and a hot end heat exchanger 22 which can exchange heat with the hot end 10b. By arranging the cold end heat exchanger 21 and the hot end heat exchanger 22 on the outer side wall, the heat exchange process between the working medium inside the Stirling compressor 10 and the cold end heat exchanger 21 and the hot end heat exchanger 22 can be more effectively managed. The gas can first flow through the cold end heat exchanger 21 to be cooled and dehumidified, and then flow through the hot end heat exchanger 22 to be heated and warmed up, which reduces heat loss and improves the thermal efficiency of the Stirling heat pump system 100.

[0046] In this embodiment, the working fluid of the Stirling compressor 10 can be helium. Helium has a high thermal conductivity, which means it can quickly transfer heat and improve heat exchange efficiency. Compared with hydrogen, which is dangerous to use, helium is an inert gas that does not react with other substances, making it very safe to use in the Stirling compressor 10 and causing no corrosion or pollution. The gas treatment device 20 circulates air, and the working fluid in the cold end 10a absorbs heat from the air flowing through the cold end heat exchanger 21, causing the temperature of the air flowing through the cold end heat exchanger 21 to drop. The moisture in the air will condense into liquid water, thereby achieving air cooling and dehumidification. The working fluid in the hot end 10b heats up during compression, and the working fluid in the hot end 10b transfers heat to the air flowing through the hot end heat exchanger 22, causing the temperature of the air flowing through the hot end heat exchanger 22 to rise, thereby providing a heat source for drying or other production process lines 200 that require hot air. The design of this embodiment allows the Stirling heat pump system 100 to effectively regulate air temperature and meet different application requirements, such as drying or dehumidification.

[0047] As shown in Figure 1 It can be understood that the Stirling compressor 10 is at least one of an α-type Stirling compressor 10, a β-type Stirling compressor 10, and a γ-type Stirling compressor 10. The α-type Stirling compressor 10 is a double-cylinder double-piston compressor with a relatively simple structure and high efficiency. The γ-type Stirling compressor 10 has two cylinders: a gas distribution cylinder and a power cylinder. In the γ-type Stirling engine, the gas distribution piston and the power piston are located in different cylinders. The β-type Stirling compressor 10 has only one cylinder with a gas distribution piston and a power piston. This structure makes the β-type Stirling compressor 10 more compact than the α-type Stirling compressor 10 and the γ-type Stirling compressor 10. In this embodiment, the Stirling compressor 10 is a β-type Stirling compressor 10. Compared with multi-cylinder designs, the β-type Stirling compressor 10 has a simpler structure, reducing the need for external piping and connections, reducing the required space, and thus reducing the potential risk of leakage and manufacturing costs. The Stirling heat pump system 100 configured in this embodiment has an output power of 10-100 kW, a power consumption of 5-40 kW, and an energy efficiency ratio of 1.5-4, which is a small-power industrial heat pump that can save energy.

[0048] Please continue to refer to Figure 1In particular, the beta-type Stirling compressor 10 comprises a cylinder 11, a slider 12, a piston 13 and a driving mechanism 14. The cylinder 11 is usually a sealed container for accommodating the piston 13 and the slider 12. The cylinder 11 provides the piston 13 and the slider 12 with a guiding function and a movement space for reciprocating movement, ensuring the accuracy and stability of the movement of the piston 13 and the slider 12.

[0049] The cylinder 11 is filled with a medium. The slider 12 is slidably arranged in the cylinder 11, and a compression chamber 111b is formed between the slider 12 and the inner wall of the cylinder 11. The working medium in the compression chamber 111b is used for heat exchange with the hot end 10b. The piston 13 is slidably arranged in the cylinder 11, and an expansion chamber 111a is formed between the piston 13, the slider 12 and the inner wall of the cylinder 11. The working medium in the compression chamber 111b is used for heat exchange with the cold end 10a. Since the slider 12 and the piston 13 are integrated in the cylinder 11, the beta-type Stirling compressor 10 occupies less space, which is convenient for installation and integration into the Stirling heat pump system 100.

[0050] The beta-type Stirling compressor 10 further comprises a driving mechanism 14 connected with the slider 12 and the piston 13. The driving mechanism 14 is used to drive the piston 13 and the slider 12 to move reciprocatingly in the cylinder 11, so as to drive the working medium to flow reciprocatingly between the compression chamber 111b and the expansion chamber 111a. The driving mechanism 14 can accurately control the movement of the piston 13 and the slider 12, and ensure the efficient reciprocating flow of the working medium between the compression chamber 111b and the expansion chamber 111a.

[0051] In some embodiments of the present application, the movement between the piston 13 and the slider 12 forms a phase angle, which affects the coordination of the movement of the piston 13 and the slider 12, and further controls the compression and expansion processes, so as to ensure that the working medium is compressed and expanded at the appropriate time. Adjustment of the phase angle can improve the working performance of the beta-type Stirling compressor 10, including increasing the output power and improving the thermal efficiency. Therefore, the driving mechanism 14 comprises a rhombus driving mechanism, which has the characteristics of high stability and uniform stress. The rhombus driving mechanism can accurately control the phase angle between the piston 13 and the slider 12, and ensure the coordination of the compression and expansion processes in the beta-type Stirling compressor 10.

[0052] In some embodiments of the present application, the phase angle between the piston 13 and the slider 12 is α, and α satisfies: 60°≤α≤90°. Exemplarily, when the phase angle α between the piston 13 and the slider 12 is 60°, the maximum stress of the rhombus driving mechanism can be reduced to achieve the highest energy efficiency. In actual operation, the phase angle between the piston 13 and the slider 12 can be adjusted according to actual requirements.

[0053] In some embodiments of the present application, the cylinder 11 comprises a cylinder body 111 and a cylinder shell 112, the sliding member 12 and the piston 13 are integrated in the cylinder body 111, and the cylinder body 111 is formed with an expansion cavity 111a and a compression cavity 111b, the cylinder shell 112 is formed with a working medium flow path, one end of the working medium flow path is communicated with the compression cavity 111b, and the other end is communicated with the expansion cavity 111a, the working medium flow path formed in the cylinder shell 112 helps to efficiently distribute the working medium and ensure smooth flow of the working medium between the compression cavity 111b and the expansion cavity 111a, thereby improving heat exchange efficiency.

[0054] The cylinder body 111 further comprises a regenerator 113, the regenerator 113 is characterized in that cold and hot fluids alternately flow through the same flow channel space, the regenerator 113 has regenerator filler, and the working medium realizes heat exchange by direct contact with the regenerator filler. From the perspective of heat exchanger, the regenerator 113 has the advantages of simple and compact structure and high heat exchange efficiency due to large volume heat capacity, large heat exchange area and small resistance along the way. The regenerator 113 is arranged on the cylinder shell 112 and can exchange heat with the working medium.

[0055] Specifically, the regenerator 113 is located between the cold end heat exchanger 21 and the hot end heat exchanger 22, and is used to reduce the temperature difference change experienced by the working medium when flowing from the hot end heat exchanger 22 to the cold end heat exchanger 21, thereby reducing heat loss. The working medium releases heat to air when flowing through the hot end heat exchanger 22, enters the regenerator 113, and releases heat again here, thereby reducing the temperature, so that the working medium can increase its ability to absorb heat from air when flowing through the cold end heat exchanger 21.

[0056] In some embodiments of the present application, the gas treatment device 20 comprises a shell 23, the shell 23 is arranged around the Stirling compressor 10, so that the whole Stirling heat pump system 100 is more compact, the floor area is reduced, and the installation and integration are facilitated. The shell 23 and the outer side wall of the Stirling compressor 10 jointly constitute a dehumidification cavity 23a and a heating cavity 23b in communication, wherein the cold end heat exchanger 21 is arranged in the dehumidification cavity 23a and connected with the cold end 10a, which helps to improve the dehumidification efficiency, because the air can more fully exchange heat with the cold end heat exchanger 21 here, reduce the air temperature and condense the moisture. The hot end heat exchanger 22 is arranged in the heating cavity 23b and connected with the hot end 10b, which helps to enhance the heating capacity, because the air can more fully absorb the heat of the hot end 10b here, thereby improving the heating efficiency.

[0057] In some embodiments of the present application, the gas treatment device 20 further comprises a liquid collecting tank 29, a drain pipe 212 and a drain valve 291, one end of the drain pipe 212 is in communication with the dehumidification cavity 23a, the other end of the drain pipe 212 is in communication with the liquid collecting tank 29, the liquid collecting tank 29 is used to collect the condensed water in the dehumidification cavity 23a, the drain valve 291 is arranged on the drain pipe 212 and located between the dehumidification cavity 23a and the liquid collecting tank 29, the drain valve 291 can open or close the flow of the condensed water in the drain pipe 212 to the liquid collecting tank 29 according to the need, and the arrangement of the drain valve 291 can also prevent the water in the liquid collecting tank 29 from flowing back to the dehumidification cavity 23a. Timely draining of the condensed water helps to maintain the dehumidification efficiency of the dehumidification cavity 23a and avoid affecting the dehumidification performance due to water accumulation in the dehumidification cavity 23a.

[0058] In some embodiments of the present application, the gas treatment device 20 further comprises an air inlet pipe 211 and a fan 24, the air inlet pipe 211 is in communication with the dehumidification cavity 23a, and the fan 24 is arranged on the air inlet pipe 211 and used to blow air into the dehumidification cavity 23a. In this embodiment, the gas is air, and the arrangement of the fan 24 can promote the flow of air and ensure that the required amount of air can flow into the dehumidification cavity 23a through the air inlet pipe 211. By adjusting the rotating speed of the fan 24, the air flow into the dehumidification cavity 23a can be controlled to meet different working conditions.

[0059] In some embodiments of the present application, the gas treatment device 20 further comprises a filter 25, the filter 25 is arranged on the air inlet pipe 211 and located upstream of the fan 24 along the air flow direction of the air inlet pipe 211, that is, the air, such as air, blown into the dehumidification cavity 23a by the fan 24, needs to pass through the filter 25 first, and the filter 25 can remove dust and particulate matter in the air entering the dehumidification cavity 23a to improve the cleanliness of the gas. Controlling the cleanliness of the inflowing gas can maintain the high efficiency of the Stirling heat pump system 100, avoid the decrease of heat exchange efficiency caused by dust accumulation, and prevent the failure of the Stirling heat pump system 100 caused by impurities in the gas.

[0060] In some embodiments of the present application, the gas treatment device 20 further comprises an air outlet pipe 221 and an adjusting valve 27, the adjusting valve 27 is arranged on the air outlet pipe 221 and used to control and adjust the flow of the gas flowing out of the heating cavity 23b, one end of the air outlet pipe 221 is in communication with the heating cavity 23b, and the other end of the air outlet pipe 221 is used to communicate with the production process line body 200, which can be a high-temperature sterilization production process, and the high-temperature gas discharged from the heating cavity 23b is used for sterilization or disinfection treatment.

[0061] As Figure 2As shown, in some embodiments of this application, the gas processing device 20 further includes a waste heat recovery unit 28. The waste heat recovery unit 28 can be used to collect and store the heat of the high-temperature air in the production line 200. By recovering and reusing the heat, the heat emission to the environment can be reduced. The waste heat recovery unit 28 has a first air inlet 281, a first air outlet 282, a second air inlet 283, and a second air outlet 284. The first air inlet 281 is connected to the dehumidification chamber 23a. The air dried in the dehumidification chamber 23a flows into the waste heat recovery unit 28 through the first air inlet 281 for heat exchange, effectively utilizing waste heat and reducing energy consumption. The first air outlet 282 is connected to the heating chamber 23b. The dried air heated by the waste heat recovery unit 28 flows into the heating chamber 23b from the first air outlet 282. The working fluid at the hot end 10b exchanges heat with the air at a high temperature, reducing the temperature gradient. A smaller temperature gradient helps improve the coefficient of performance (COP) of the Stirling heat pump system 100 because increased heat exchange efficiency reduces the energy required to achieve a specific output, thus improving the efficiency of the heat exchanger. The second inlet end 283 is connected to the outlet end of the production line 200. Gas flowing out of the production line 200 flows into the waste heat recovery unit 28 through the second inlet end 283. The second outlet end 284 is connected to the outside air or to the inlet pipe 211, allowing for flexible exhaust options. That is, the gas flowing out from the second outlet end 284 can be directly discharged into the outside air or returned to the gas handling device 20 for recirculation after passing through the filter element 25. When the temperature of the air discharged from the second outlet end 284 is lower than the set temperature of the dehumidification chamber 23a, and the second outlet end 284 is connected to the inlet pipe 211, the dehumidification efficiency in the dehumidification chamber 23a can be improved.

[0062] like Figure 1 As shown, to prevent sudden airflow changes, in some embodiments of this application, the gas handling device 20 further includes a buffer 26, which is disposed in the inlet pipe 211 and located between the fan 24 and the dehumidification chamber 23a. If the gas flows directly into the dehumidification chamber 23a through the inlet pipe 211, the flow rate will be too high. The buffer 26 helps to slow down the gas flow rate, ensuring a smooth flow of gas into the dehumidification chamber 23a. A smooth airflow reduces impact and wear on the interior of the dehumidification chamber 23a, extending the service life of the Stirling heat pump system 100. Furthermore, when the second outlet end 284 is connected to the inlet pipe 211, a portion of the gas flowing out of the gas handling device 20 can be recovered and flow into the dehumidification chamber 23a. Then, a portion of outside air is blown in by the fan 24. The buffer 26 also allows for pre-mixing and homogenization of the outside air blown in with the high-temperature air flowing into the second outlet end 284.

[0063] In some embodiments of the present application, the gas processing device 20 further comprises a secondary waste heat recovery device, which can also be used to collect and store the heat of the high-temperature air in the production process line 200. The secondary waste heat recovery device is located between the buffer 26 and the cold end heat exchanger 21, and is used to heat the gas output from the buffer 26 to preheat the gas before it flows into the dehumidification chamber 23a. After the primary preheating is completed, the gas enters the dehumidification chamber 23a to form dry air, and the dry air flows into the waste heat recovery device 28 for secondary preheating. The air flowing out of the dehumidification chamber 23a has been preheated twice before it is transmitted to the heating chamber 23b, so that the preheated gas can reach the required working temperature more quickly, shorten the production cycle and improve the production efficiency.

[0064] Please continue to refer to Figure 1 To adjust the temperature of the air in the dehumidification chamber 23a and the heating chamber 23b, in some embodiments of the present application, the beta Stirling compressor 10 further comprises a first telescopic member 15 and a second telescopic member 16. The first telescopic member 15 is telescopically arranged on the piston 13 to change the volume of the expansion chamber 111a. When the first telescopic member 15 extends relative to the piston 13, the volume of the expansion chamber 111a decreases, which means that the volume of the working medium is compressed during the expansion process, resulting in an increase in pressure, which improves the efficiency of heat transfer from the working medium to the wall of the cold end heat exchanger 21, i.e. the dehumidification chamber 23a, thereby causing the temperature of the air in the dehumidification chamber 23a to decrease. When the first telescopic member 15 is retracted relative to the piston 13, the volume of the expansion chamber 111a increases, which means that the working medium can expand more fully in the expansion chamber 111a, which will result in a relatively lower pressure and a lower heat exchange efficiency between the working medium and the dehumidification chamber 23a than when the first telescopic member 15 extends relative to the piston 13, thereby causing the temperature of the air in the dehumidification chamber 23a to be higher than when the first telescopic member 15 extends relative to the piston 13.

[0065] The second telescopic member 16 is telescopically arranged on the sliding member 12 to change the volume of the compression chamber 111b. When the second telescopic member 16 extends relative to the sliding member 12, the volume of the compression chamber 111b decreases, which means that the working medium is subjected to greater compression force during the compression process, resulting in an increase in temperature and pressure. Since the working medium absorbs heat during the compression process, its temperature increases, and when it flows through the hot end 10b, it can transfer more heat to the air in the heating chamber 23b.

[0066] The temperature of the air in the heating chamber 23b increases. When the second telescopic member 16 is retracted relative to the sliding member 12, the volume of the compression chamber 111b increases. The increased volume means that the compression force experienced by the working medium during compression is reduced, resulting in a relative decrease in its temperature and pressure. The working medium absorbs less heat during compression, so the heat transferred from the hot end 10b to the heating chamber 23b is also reduced, i.e. the air temperature in the heating chamber 23b is lower than when the second telescopic member 16 is extended relative to the sliding member 12.

[0067] Since the cylinder 11 of the working medium cycle is a closed space, the amount of working medium filled inside is constant, by adjusting the extension and retraction of the first telescopic member 15 and the second telescopic member 16, the total volume and ratio of the compression chamber 111b and the expansion chamber 111a can be adjusted, the temperature of the gas in the dehumidification chamber 23a and the heating chamber 23b can be controlled to meet different application requirements. A flexible and effective way is provided to manage the gas temperature in the Stirling heat pump system 100, optimize the heat exchange process, and improve the energy efficiency and performance of the entire system.

[0068] Understandably, the first telescopic member 15 is telescopic along the driving direction of the axial mechanism relative to the piston 13, which reduces the complexity of mechanical components, can reduce the friction and wear of the first telescopic member 15 and the piston 13, and allows precise control of the volume of the expansion chamber 111a, which helps to accurately adjust the temperature of the dehumidification chamber 23a. Of course, the first telescopic member 15 can also be telescopic inclined to the axial direction of the cylinder 11, which is not limited in the present application.

[0069] The second telescopic member 16 is telescopic along the driving direction of the driving mechanism 14 relative to the sliding member 12, which can reduce the friction and wear of the second telescopic member 16 and the sliding member 12, and allows precise control of the volume of the compression chamber 111b, which helps to accurately adjust the temperature of the heating chamber 23b. As above, the second telescopic member 16 can also be telescopic inclined to the axial direction of the cylinder 11, which is not limited in the present application.

[0070] As shown in Figure 4 The present application provides a control method of a Stirling heat pump system, applied to the Stirling heat pump system of any of the above embodiments, the control method comprising:

[0071] S100, obtaining a target output parameter of the Stirling heat pump system;

[0072] S200, adjusting the volume of the compression chamber and / or the expansion chamber of the Stirling compressor according to the target output parameter.

[0073] In the embodiment, the target output parameters such as the gas temperature of the dehumidification cavity and the gas temperature of the heating cavity can be obtained according to the user's requirements, and the gas temperature of the dehumidification cavity and the gas temperature of the heating cavity of the Stirling heat pump system can be ensured to meet the expected target by adjusting the volumes of the compression cavity and / or the expansion cavity. That is, the Stirling heat pump system can adapt to different requirement changes, providing greater operational flexibility. The control method provided in the embodiment can realize automatic control, reduce manual intervention, and improve operational convenience and accuracy.

[0074] In some embodiments of the present application, the target output parameter includes a target output gear, and the step of adjusting the volumes of the compression cavity and / or the expansion cavity of the Stirling compressor according to the target output parameter includes:

[0075] S211, obtaining the current gear of the Stirling heat pump system;

[0076] S212, when the current gear is lower than the target output gear, reducing the volume of the compression cavity, and / or, increasing the volume of the expansion cavity;

[0077] S213, when the current gear is higher than the target output gear, increasing the volume of the compression cavity, and / or, reducing the volume of the expansion cavity.

[0078] For example, the Stirling heat pump system of the embodiment has three gears, and the temperature of the heating cavity gradually decreases from the low gear one to the high gear three. The current gear of the Stirling heat pump system is obtained as two gears. When the target output gear of the user is one gear, that is, the current gear is lower than the target output gear, the volume of the compression cavity is reduced, the ratio of the compression cavity to the expansion cavity is reduced, and the gas temperature in the heating cavity is higher than that when the gear is two. In another embodiment, to increase the gas temperature in the heating cavity, the volume of the expansion cavity can also be increased, so that the ratio of the compression cavity to the expansion cavity is reduced. Understandably, the volume of the compression cavity can also be reduced and the volume of the expansion cavity can also be increased at the same time, so that the ratio of the compression cavity to the expansion cavity is also reduced, so that the gas temperature in the heating cavity is increased to the target output gear one.

[0079] When the target output gear of the user is three gears, that is, the current gear is higher than the target output gear, the volume of the compression cavity of the Stirling compressor is increased, the ratio of the compression cavity to the expansion cavity is increased, and the gas temperature in the heating cavity is lower than that when the gear is two. In another embodiment, to reduce the gas temperature in the heating cavity, the volume of the expansion cavity can also be reduced, so that the ratio of the compression cavity to the expansion cavity is increased. Understandably, the volume of the compression cavity can also be increased and the volume of the expansion cavity can also be reduced at the same time, so that the ratio of the compression cavity to the expansion cavity is also increased, so that the gas temperature in the heating cavity is reduced to the target output gear three.

[0080] The embodiment only needs to set a target output gear, and the Stirling heat pump system can automatically adjust to a corresponding state, simplifying the operation process, reducing the error of the operation, and improving the reliability of the system.

[0081] In some embodiments of the present application, the volume of the expansion chamber can be changed by adjusting the extension amount of the first telescopic member, and the volume of the compression chamber can be changed by adjusting the extension amount of the second telescopic member. In the embodiment, the temperature of the heating chamber in the low gear (gear 1) is 120℃, and the temperature of the dehumidification chamber is 7℃. The gear 1 is suitable for high-temperature sterilization and heating and dehumidification working conditions. The temperature of the heating chamber in the medium gear (gear 2) is 80℃, and the temperature of the dehumidification chamber is 1℃. The gear 2 is suitable for most drying working conditions. The temperature of the heating chamber in the high gear (gear 3) is 40℃, and the temperature of the dehumidification chamber is -10℃. The gear 3 can open the secondary waste heat recovery device.

[0082] When the current gear of the Stirling heat pump system is gear 2 and the target output gear of the user is gear 1, the second telescopic member is controlled to extend to the upper limit value, and the first telescopic member is controlled to retract to the lower limit value. At this time, the volume of the compression chamber is the minimum value, and the volume of the expansion chamber is the maximum value, so that the temperature of the heating chamber reaches 120℃, and the temperature of the dehumidification chamber reaches 7℃.

[0083] When the target output gear of the user is gear 3, the second telescopic member is controlled to retract to the lower limit value, and the first telescopic member is controlled to extend to the upper limit value. At this time, the volume of the compression chamber is the maximum value, and the volume of the expansion chamber is the minimum value, so that the temperature of the heating chamber reaches 40℃, and the temperature of the dehumidification chamber reaches -10℃.

[0084] In some embodiments of the present application, the target output parameter includes a target output temperature, and the step of adjusting the volume of the compression chamber and / or the expansion chamber of the Stirling compressor according to the target output temperature includes:

[0085] S221, acquiring the current temperature of the gas output by the Stirling heat pump system;

[0086] S222, when the current temperature is less than the target output temperature, reducing the volume of the compression chamber and / or increasing the volume of the expansion chamber;

[0087] S223, when the current temperature is greater than the target output temperature, increasing the volume of the compression chamber and / or reducing the volume of the expansion chamber.

[0088] In the embodiment, the target output temperature is acquired to correspondingly adjust the volume of the compression chamber and / or the expansion chamber, that is, the Stirling heat pump system can realize stepless adjustment of the temperature of the gas in the dehumidification chamber and the heating chamber. The stepless adjustment provides a continuous temperature control range, increases the adaptability and flexibility of the Stirling heat pump system, and can provide a more comfortable temperature environment for application scenarios that require a specific temperature, such as indoor heating or specific industrial processes.

[0089] In some embodiments of the present application, a temperature sensor can be arranged at the outlet of the heating cavity to monitor the temperature of the gas discharged from the heating cavity of the Stirling heat pump system in real time, so as to provide a reference for the user when setting the target output temperature.

[0090] For example, the current temperature is 80℃ and the target output temperature is 120℃, i.e. the current temperature is less than the target output temperature. By gradually reducing the volume of the compression cavity, the ratio of the compression cavity to the expansion cavity is gradually reduced, and the temperature of the gas in the heating cavity is increased compared with the current temperature. When the temperature sensor detects that the outlet temperature of the heating cavity reaches the target output temperature 120℃, the volume of the compression cavity is no longer reduced, and the target output temperature is maintained. In another embodiment, to increase the temperature of the gas in the heating cavity, the volume of the expansion cavity can also be gradually increased, so that the ratio of the compression cavity to the expansion cavity is reduced. Understandably, the volume of the compression cavity can also be gradually reduced and the volume of the expansion cavity can also be gradually increased at the same time, which can also achieve the reduction of the ratio of the compression cavity to the expansion cavity, so that the temperature of the gas in the heating cavity is increased to the target output temperature 120℃.

[0091] For example, the current temperature is 80℃ and the target output temperature is 120℃, i.e. the current temperature is less than the target output temperature. By gradually reducing the volume of the compression cavity, the ratio of the compression cavity to the expansion cavity is gradually reduced, and the temperature of the gas in the heating cavity is increased compared with the current temperature. When the temperature sensor detects that the outlet temperature of the heating cavity reaches the target output temperature 120℃, the volume of the compression cavity is no longer reduced, and the target output temperature is maintained. In another embodiment, to increase the temperature of the gas in the heating cavity, the volume of the expansion cavity can also be gradually increased, so that the ratio of the compression cavity to the expansion cavity is reduced. Understandably, the volume of the compression cavity can also be gradually reduced and the volume of the expansion cavity can also be gradually increased at the same time, which can also achieve the reduction of the ratio of the compression cavity to the expansion cavity, so that the temperature of the gas in the heating cavity is increased to the target output temperature 120℃.

[0092] In the description of the present application, it should be understood that the orientation or position relationship indicated by the terms "up", "down", "left", "right" and the like is based on the orientation or position relationship shown in the drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, therefore the terms describing the position relationship in the drawings are only used for exemplary illustration, and cannot be understood as a limitation of the present patent. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0093] In addition, the terms "first", "second", etc. are used only for descriptive purposes and do not connote or imply relative importance or implicitly indicate the number of technical features indicated. Thus, features defined with "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "a plurality of" is at least two, for example, two, three, etc., unless otherwise explicitly specified and limited.

[0094] In the description of the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connecting", "fixing" and other terms should be understood broadly, for example, can be fixedly connected, can be detachably connected, or integrated; can be mechanically connected, or electrically connected; can be directly connected, or indirectly connected through an intermediate medium; can be the internal communication of two elements or the interaction relationship of two elements, unless otherwise explicitly limited. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0095] It should be noted that when an element is referred to as "fixed to" or "disposed on" another element, it can be directly on another element or there can be a middle element. When an element is considered to be "connected" to another element, it can be directly connected to another element or there can be a middle element. The terms "vertical", "horizontal", "up", "down", "left", "right" and similar expressions used herein are for illustrative purposes only and are not the only implementation.

[0096] The above is only a specific implementation of the present application, but the protection scope of the present application is not limited thereto, any skilled in the art within the technical scope disclosed in the present application, can easily think of changes or replacements, should be covered in the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A Stirling heat pump system, characterised in that, The application relates to a beta-type Stirling compressor and a gas treatment device. The beta-type Stirling compressor comprises: a cylinder filled with a working medium; a sliding element slidably arranged in the cylinder, a compression cavity being formed between the sliding element and the inner wall of the cylinder, and the working medium in the compression cavity being used for heat exchange with the hot end; a piston slidably arranged in the cylinder, an expansion cavity being formed between the piston, the sliding element and the inner wall of the cylinder, and the working medium in the expansion cavity being used for heat exchange with the cold end; a driving mechanism connected with the sliding element and the piston, the driving mechanism being used for driving the piston and the sliding element to make reciprocating linear motion in the cylinder, so as to drive the working medium to reciprocate between the compression cavity and the expansion cavity; a first telescopic element telescopically arranged on the piston, so as to change the volume of the expansion cavity; and a second telescopic element telescopically arranged on the sliding element, so as to change the volume of the compression cavity. The gas treatment device comprises: a shell arranged around the beta-type Stirling compressor, the shell and the outer wall of the beta-type Stirling compressor jointly constituting a dehumidification cavity and a heating cavity in communication; wherein the cold end heat exchanger is arranged in the dehumidification cavity and connected with the cold end, and the hot end heat exchanger is arranged in the heating cavity and connected with the hot end.

2. A Stirling heat pump system according to claim 1, characterised in that The gas treatment device further comprises: an air inlet pipeline in communication with the dehumidification cavity; and a fan arranged on the air inlet pipeline and used for blowing the gas into the dehumidification cavity.

3. A Stirling heat pump system according to claim 2, characterised in that, The gas treatment device further comprises: a filter arranged on the air inlet pipeline and located upstream of the fan along the air flow direction of the air inlet pipeline; and / or a buffer arranged on the air inlet pipeline and located between the fan and the dehumidification cavity.

4. A Stirling heat pump system according to claim 3, characterised in that, The gas treatment device further comprises: an air outlet pipeline having one end in communication with the heating cavity and the other end used for being in communication with a production process line; and an adjusting valve arranged on the air outlet pipeline.

5. A Stirling heat pump system according to claim 3, wherein The gas treatment device further comprises: a waste heat recovery device having a first air inlet end, a first air outlet end, a second air inlet end and a second air outlet end, the first air inlet end being in communication with the dehumidification cavity, the first air outlet end being in communication with the heating cavity, the second air inlet end being in communication with the production process line, and the second air outlet end being in communication with external air or the air inlet pipeline. The gas treatment device further comprises:

6. A Stirling heat pump system according to claim 5, characterised in that, a liquid collecting tank, a drain pipeline having one end in communication with the dehumidification cavity and the other end in communication with the liquid collecting tank; and 7. A Stirling heat pump system as claimed in claim 2, characterised in that, a drain valve arranged on the drain pipeline and located between the dehumidification cavity and the liquid collecting tank. The cylinder comprises: ​ ​ 8. The Stirling heat pump system of claim 1 wherein, ​ a cylinder body, the sliding member and the piston are arranged in the cylinder body, and the cylinder body is formed with the expansion chamber and the compression chamber; a cylinder shell formed with a working medium flow path, one end of the working medium flow path being communicated with the compression chamber and the other end being communicated with the expansion chamber; and a regenerator arranged on the cylinder shell and capable of exchanging heat with the working medium.

9. The Stirling heat pump system of claim 1 wherein, the first telescopic member is telescopic relative to the piston along the driving direction of the driving mechanism; and / or the second telescopic member is telescopic relative to the sliding member along the driving direction of the driving mechanism.

10. A Stirling heat pump system as claimed in claim 1, characterized in that the phase angle between the piston and the sliding member is α, and the α satisfies 60°≤α≤90°; and / or the driving mechanism comprises a rhombus driving mechanism.

11. A control method of a Stirling heat pump system, characterized by, The control method is applied to the Stirling heat pump system according to any one of claims 1-10, and the control method comprises: obtaining a target output parameter of the Stirling heat pump system; adjusting the volume of the compression chamber and / or the expansion chamber of the β-type Stirling compressor according to the target output parameter.

12. The control method according to claim 11, characterized by, The target output parameter comprises a target output gear, and the step of adjusting the volume of the compression chamber and / or the expansion chamber of the β-type Stirling compressor according to the target output parameter comprises: obtaining a current gear of the Stirling heat pump system; when the current gear is lower than the target output gear, reducing the volume of the compression chamber and / or increasing the volume of the expansion chamber; when the current gear is higher than the target output gear, increasing the volume of the compression chamber and / or reducing the volume of the expansion chamber.

13. The control method according to claim 12, characterized by, The target output parameter comprises a target output temperature, and the step of adjusting the volume of the compression chamber and / or the expansion chamber of the β-type Stirling compressor according to the target output temperature comprises: obtaining a current temperature of the gas output by the Stirling heat pump system; when the current temperature is lower than the target output temperature, reducing the volume of the compression chamber and / or increasing the volume of the expansion chamber; when the current temperature is higher than the target output temperature, increasing the volume of the compression chamber and / or reducing the volume of the expansion chamber.

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